US9856885B2 - Oil tank of turbo chiller compressor and turbo chiller compressor - Google Patents

Oil tank of turbo chiller compressor and turbo chiller compressor Download PDF

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Publication number
US9856885B2
US9856885B2 US14/768,326 US201414768326A US9856885B2 US 9856885 B2 US9856885 B2 US 9856885B2 US 201414768326 A US201414768326 A US 201414768326A US 9856885 B2 US9856885 B2 US 9856885B2
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Prior art keywords
turbo chiller
oil tank
heater
compressor
bottom plate
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US14/768,326
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US20160010654A1 (en
Inventor
Yasushi Hasegawa
Kenji Ueda
Masataka Yanagita
Masayoshi Mikuriya
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Assigned to MITSUBISHI HEAVY INDUSTRIES, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HASEGAWA, YASUSHI, MIKURIYA, Masayoshi, UEDA, KENJI, YANAGITA, Masataka
Publication of US20160010654A1 publication Critical patent/US20160010654A1/en
Assigned to MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MITSUBISHI HEAVY INDUSTRIES, LTD.
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5853—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps heat insulation or conduction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication

Definitions

  • the present invention relates to an oil tank of a turbo chiller compressor and to a turbo chiller compressor.
  • Examples of an oil tank of a turbo chiller compressor include an oil tank 13 including a heater 30 as illustrated in FIG. 2 of PTL 1, and an oil tank chamber 2 including an oil heater 6 as illustrated in FIGS. 1(A) and 2(A) of PTL 2.
  • the heater 30 or the oil heater 6 needs to be replaced due to a trouble thereof, the heater 30 or the oil heater 6 needs to be replaced after all of oil in the oil tank 13 or the oil tank chamber 2 and refrigerant in a turbo chiller are removed.
  • the present invention has been made to solve the above-described problem, and is intended to provide an oil tank of a turbo chiller compressor whose heater can be replaced or checked without removing oil from the oil tank and removing refrigerant from a turbo chiller and to provide a turbo chiller compressor.
  • the present invention employs the following solutions.
  • a first aspect of the present invention is intended for an oil tank of a turbo chiller compressor, including a bottom plate, and a side plate standing upright so as to extend upward from an outer peripheral edge portion of the bottom plate.
  • the oil tank forms a bottom portion of a casing forming the turbo chiller compressor, a through-hole is formed so as to penetrate the side plate in a plate thickness direction, a protective tube closed at a tip end thereof is inserted into the through-hole, and a rod-shaped heater configured to be able to be pulled out from the protective tube and be inserted into the protective tube is inserted into the protective tube.
  • the heater is replaced or checked only by pulling out of the heater from the protective tube and insertion of the heater into the protective tube. That is, the heater is replaced or checked in the state in which the protective tube remains fixed to the side plate forming the oil tank.
  • the heater can be replaced or checked without removing oil from the oil tank and removing refrigerant from a turbo chiller.
  • the through-hole is more preferably formed at a bottommost portion of the side plate.
  • a space between the protective tube and the heater is more preferably filled with heat transfer fluid having a high coefficient of thermal conductivity.
  • the coefficient of thermal conductivity from the heater to the protective tube can be increased, and therefore, a low-power heater can be employed.
  • a second aspect of the present invention is intended for an oil tank of a turbo chiller compressor, including a bottom plate, and a side plate standing upright so as to extend upward from an outer peripheral edge portion of the bottom plate.
  • the oil tank forms a bottom portion of a casing forming the turbo chiller compressor, in the bottom plate, a hole is formed so as to extend from one end surface of the bottom plate toward the other end surface of the bottom plate opposite to the one end surface, and a rod-shaped heater configured to be able to be pulled out from the hole and be inserted into the hole is inserted into the hole.
  • the heater is replaced or checked only by pulling out of the heater from the hole formed inside the bottom plate and insertion of the heater into the hole.
  • the heater can be replaced or checked without removing oil from the oil tank and removing refrigerant from a turbo chiller.
  • a space between the hole and the heater is more preferably filled with heat transfer fluid 88 having a high coefficient of thermal conductivity.
  • the coefficient of thermal conductivity from the heater to the bottom plate can be increased, and therefore, a low-power heater can be employed.
  • a third aspect of the present invention is intended for an oil tank of a turbo chiller compressor, including a bottom plate, and a side plate standing upright so as to extend upward from an outer peripheral edge portion of the bottom plate.
  • the oil tank forms a bottom portion of a casing forming the turbo chiller compressor, and a sheet-shaped heater is attached so as to cover an outer surface of the bottom plate or cover outer surfaces of the bottom and side plates.
  • the heater is replaced or checked only by detachment and attachment of the heater attached to the outer surface of the bottom plate or the outer surfaces of the bottom and side plates.
  • the heater can be replaced or checked without removing oil from the oil tank and removing refrigerant from a turbo chiller.
  • sheet-shaped metal having a high coefficient of thermal conductivity is more preferably interposed between the heater and the outer surface so as to closely adhere to both of the heater and the outer surface.
  • the coefficient of thermal conductivity from the heater to an outer surface of the oil tank can be increased, and therefore, a low-power heater can be employed.
  • a plurality of heat transfer fins are more preferably formed so as to protrude upward from an upper surface of the bottom plate.
  • the contact area between oil and the bottom plate heated by the heater can be increased.
  • oil can be more efficiently heated, and as a result, a lower-power heater can be employed.
  • a fourth aspect of the present invention is intended for a turbo chiller compressor including the oil tank of a turbo chiller compressor of any one of the above-described aspects.
  • the heater attached to the oil tank can be replaced or checked without removing oil from the oil tank and removing refrigerant from a turbo chiller.
  • the heater attached to the oil tank can be replaced or checked without removing oil from the oil tank and removing refrigerant from the turbo chiller, a working time required for replacement or checking of the heater can be significantly reduced, and therefore, the operation rate and reliability of the turbo chiller compressor can be improved.
  • a fifth aspect of the present invention is intended for a turbo chiller including the turbo chiller compressor described above.
  • the heater can be replaced or checked without removing oil from the oil tank and removing refrigerant from the turbo chiller.
  • FIG. 1 is a partial cross-sectional view illustrating an oil tank of a turbo chiller compressor according to a first embodiment of the present invention.
  • FIG. 2 is a partial cross-sectional view illustrating an oil tank of a turbo chiller compressor according to a second embodiment of the present invention.
  • FIG. 3 is a partial cross-sectional view illustrating an oil tank of a turbo chiller compressor according to a third embodiment of the present invention.
  • FIG. 4 is a partial cross-sectional view illustrating an oil tank of a turbo chiller compressor according to a fourth embodiment of the present invention.
  • An oil tank of a turbo chiller compressor of a first embodiment of the present invention, a turbo chiller compressor including the oil tank of the turbo chiller compressor of the first embodiment of the present invention, and a turbo chiller including the turbo chiller compressor of the first embodiment of the present invention will be described below with reference to FIG. 1 .
  • a turbo chiller 1 A of the present embodiment is, for example, placed at a building or a factory in order to generate coolant water for adjusting air.
  • the turbo chiller 1 A includes a turbo chiller compressor (a turbo compressor) 3 A rotatably driven by an electric motor 2 to compress refrigerant vapor into high-pressure vapor, an evaporator (not shown) configured to evaporate chilled water, a condenser (not shown) configured to cool high-pressure vapor with coolant water to condense the high-pressure vapor, and an expander (not shown) configured to expand, by reducing the pressure of condensed refrigerant, the condensed refrigerant to send the expanded refrigerant to the evaporator.
  • the turbo chiller compressor 3 A, the evaporator, the condenser, and the expander are connected together with refrigerant pipes (not shown) through which refrigerant circulates.
  • An oil tank 10 of the turbo chiller compressor 3 A includes a bottom plate 11 , a (first) side plate 12 , a (second) side plate 13 , a (third) side plate (not shown), and a (fourth) side plate (not shown), these side plates standing upright so as to extend upward from an outer peripheral edge portion of the bottom plate 11 .
  • These bottom and side plates form a bottom portion (a lower portion) of a (first) casing 14 (in the present embodiment, a compressor casing forming the turbo chiller compressor 3 A).
  • the bottom plate 11 is a plate-shaped member extending in an axial direction and a right-left direction and having a rectangular shape as viewed in the plane.
  • the side plate 12 is a plate-shaped member positioned on a side close to a (second) casing 15 (in the present embodiment, a motor casing forming the electric motor 2 ) attached to one end of the casing 14 and extending in the vertical direction.
  • a (second) casing 15 in the present embodiment, a motor casing forming the electric motor 2
  • the side plate 13 is a plate-shaped member positioned on a side close to a (third) casing 16 (in the present embodiment, a compressor inlet casing forming an inlet of the turbo chiller compressor 3 A) attached to the other end of the casing 14 and extending in the vertical direction.
  • a (third) casing 16 in the present embodiment, a compressor inlet casing forming an inlet of the turbo chiller compressor 3 A
  • a through-hole 21 is formed so as to penetrate, in a plate thickness direction, through a bottom portion (a lower portion) of the side plate 12 , and more preferably a bottommost portion (a lowermost portion) of the side plate 12 .
  • the through-hole 21 is formed with a (first) through-hole 24 which is positioned on the near side (the outside) of the side plate 12 and which receives an external thread portion of a screw joint 23 provided at a base end portion of a protective tube 22 and a (second) through-hole 25 which is positioned on the far side (the inside) of the side plate 12 and into which the protective tube 22 is inserted.
  • An internal thread portion which comes into engagement with the external thread portion formed at an outer peripheral surface of the screw joint 23 is formed at an inner peripheral surface of the through-hole 24 .
  • a heater 26 is inserted into the protective tube 22 , and a space between the protective tube 22 and the heater 26 is filled with heat transfer fluid 88 (e.g., a heat-resistant release silicon material, chemically-synthesized oil, and a boron nitride aqueous solution) having a high coefficient of thermal conductivity (having excellent thermal conductivity).
  • heat transfer fluid 88 e.g., a heat-resistant release silicon material, chemically-synthesized oil, and a boron nitride aqueous solution
  • a reference numeral “ 27 ” in FIG. 1 denotes oil (lubrication oil).
  • the heater 26 is replaced or checked only by pulling out of the heater 26 from the protective tube 22 and insertion of the heater 26 into the protective tube 22 . That is, the heater 26 is replaced or checked in the state in which the protective tube 22 remains fixed to the side plate 12 forming the oil tank 10 .
  • the heater 26 can be replaced or checked without removing the oil 27 from the oil tank 10 and removing refrigerant from the turbo chiller 1 A.
  • the through-hole 21 is formed at the bottommost portion of the side plate 12 .
  • convection of the oil 27 heated by the heater 26 can be promoted, and therefore, the oil 27 in the oil tank 10 can be efficiently heated.
  • the space between the protective tube 22 and the heater 26 is filled with the heat transfer fluid 88 having a high coefficient of thermal conductivity.
  • the coefficient of thermal conductivity from the heater 26 to the protective tube 22 can be increased, and therefore, a low-power heater can be employed.
  • the heater 26 attached to the oil tank 10 can be replaced or checked without removing the oil 27 from the oil tank 10 and removing refrigerant from the turbo chiller 1 A.
  • turbo chiller compressor 3 A of the present embodiment since the heater 26 attached to the oil tank 10 can be replaced or checked without removing the oil 27 from the oil tank 10 and removing refrigerant from the turbo chiller 1 A, a working time required for replacement or checking of the heater 26 can be significantly reduced, and therefore, the operation rate and reliability of the turbo chiller compressor 3 A can be improved.
  • the working time required for replacement or checking of the heater 26 attached to the oil tank 10 of the turbo chiller compressor 3 A is significantly reduced.
  • the operation rate and reliability of the turbo chiller 1 A can be improved.
  • An oil tank of a turbo chiller compressor of a second embodiment of the present invention, a turbo chiller compressor including the oil tank of the turbo chiller compressor of the second embodiment of the present invention, and a turbo chiller including the turbo chiller compressor of the second embodiment of the present invention will be described below with reference to FIG. 2 .
  • a turbo chiller 1 B of the present embodiment is, for example, placed at a building or a factory in order to generate coolant water for adjusting air.
  • the turbo chiller 1 B includes a turbo chiller compressor (a turbo compressor) 3 B rotatably driven by an electric motor 2 to compress refrigerant vapor into high-pressure vapor, an evaporator (not shown) configured to evaporate chilled water, a condenser (not shown) configured to cool high-pressure vapor with coolant water to condense the high-pressure vapor, and an expander (not shown) configured to expand, by reducing the pressure of condensed refrigerant, the condensed refrigerant to send the expanded refrigerant to the evaporator.
  • the turbo chiller compressor 3 B, the evaporator, the condenser, and the expander are connected together with refrigerant pipes (not shown) through which refrigerant circulates.
  • an oil tank 30 of the turbo chiller compressor 3 B of the present embodiment includes a bottom plate 31 , a (first) side plate 32 , a (second) side plate 33 , a (third) side plate (not shown), and a (fourth) side plate (not shown), these side plates standing upright so as to extend upward from an outer peripheral edge portion of the bottom plate 31 .
  • These bottom and side plates form a bottom portion (a lower portion) of a (first) casing 34 (in the present embodiment, a compressor casing forming the turbo compressor 3 B).
  • the bottom plate 31 is a plate-shaped member extending in an axial direction and a right-left direction and having a rectangular shape as viewed in the plane.
  • the side plate 32 is a plate-shaped member positioned on a side close to a (second) casing 15 (in the present embodiment, a motor casing forming the electric motor 2 ) attached to one end of the casing 34 and extending in the vertical direction.
  • a (second) casing 15 in the present embodiment, a motor casing forming the electric motor 2
  • the side plate 33 is a plate-shaped member positioned on a side close to a (third) casing 16 (in the present embodiment, a compressor inlet casing forming an inlet of the turbo compressor 3 B) attached to the other end of the casing 34 and extending in the vertical direction.
  • a (third) casing 16 in the present embodiment, a compressor inlet casing forming an inlet of the turbo compressor 3 B
  • a hole 41 is formed so as to extend, in the axial direction, from a vertically-extending end surface of the bottom plate 31 positioned on the side close to the casing 15 toward a vertically-extending end surface of the bottom plate 31 positioned on the side close to the casing 16 .
  • the hole 41 is formed with a (first) hole 44 which is positioned on the near side (the side close to the casing 15 ) of the bottom plate 31 and which receives an external thread portion of a screw joint 43 provided at a base end portion of a rod-shaped (electric) heater (a heating means) 42 and a (second) hole 45 which is positioned on the far side (the far side of the hole 44 ) of the bottom plate 31 and into which the heater 42 is inserted.
  • a (first) hole 44 which is positioned on the near side (the side close to the casing 15 ) of the bottom plate 31 and which receives an external thread portion of a screw joint 43 provided at a base end portion of a rod-shaped (electric) heater (a heating means) 42 and a (second) hole 45 which is positioned on the far side (the far side of the hole 44 ) of the bottom plate 31 and into which the heater 42 is inserted.
  • An internal thread portion which comes into engagement with the external thread portion formed at an outer peripheral surface of the screw joint 43 is formed at an inner peripheral surface of the hole 44 .
  • a heater 42 is inserted into the hole 41 , and a space between the hole 41 and the heater 42 is filled with heat transfer fluid 88 (e.g., a heat-resistant release silicon material, chemically-synthesized oil, and a boron nitride aqueous solution) having a high coefficient of thermal conductivity (having excellent thermal conductivity).
  • heat transfer fluid 88 e.g., a heat-resistant release silicon material, chemically-synthesized oil, and a boron nitride aqueous solution having a high coefficient of thermal conductivity (having excellent thermal conductivity).
  • a reference numeral “ 46 ” in FIG. 2 denotes oil(lubrication oil).
  • the heater 42 is replaced or checked only by pulling out of the heater 42 from the hole 41 formed inside the bottom plate 31 and insertion of the heater 42 into the hole 41 .
  • the heater 42 can be replaced or checked without removing the oil 46 from the oil tank 30 and removing refrigerant from the turbo chiller 1 B.
  • the space between the hole 41 and the heater 42 is filled with the heat transfer fluid 88 having a high coefficient of thermal conductivity.
  • the coefficient of thermal conductivity from the heater 42 to the bottom plate 31 can be increased, and therefore, a low-power heater can be employed.
  • the heater 42 attached to the oil tank 30 can be replaced or checked without removing the oil 46 from the oil tank 30 and removing refrigerant from the turbo chiller 1 B.
  • turbo chiller compressor 3 B of the present embodiment since the heater 42 attached to the oil tank 30 can be replaced or checked without removing the oil 46 from the oil tank 30 and removing refrigerant from the turbo chiller 1 B, a working time required for replacement or checking of the heater 42 can be significantly reduced, and therefore, the operation rate and reliability of the turbo chiller compressor 3 B can be improved.
  • the working time required for replacement or checking of the heater 42 attached to the oil tank 30 of the turbo chiller compressor 3 B is significantly reduced.
  • the operation rate and reliability of the turbo chiller 1 B can be improved.
  • An oil tank of a turbo chiller compressor of a third embodiment of the present invention, a turbo chiller compressor including the oil tank of the turbo chiller compressor of the third embodiment of the present invention, and a turbo chiller including the turbo chiller compressor of the third embodiment of the present invention will be described below with reference to FIG. 3 .
  • a turbo chiller 1 C of the present embodiment is, for example, placed at a building or a factory in order to generate coolant water for adjusting air.
  • the turbo chiller 1 C includes a turbo chiller compressor (a turbo compressor) 3 C rotatably driven by an electric motor 2 to compress refrigerant vapor into high-pressure vapor, an evaporator (not shown) configured to evaporate chilled water, a condenser (not shown) configured to cool high-pressure vapor with coolant water to condense the high-pressure vapor, and an expander (not shown) configured to expand, by reducing the pressure of condensed refrigerant, the condensed refrigerant to send the expanded refrigerant to the evaporator.
  • the turbo chiller compressor 3 C, the evaporator, the condenser, and the expander are connected together with refrigerant pipes (not shown) through which refrigerant circulates.
  • an oil tank 50 of the turbo chiller compressor 3 C of the present embodiment includes a bottom plate 51 , a (first) side plate 52 , a (second) side plate 53 , a (third) side plate 54 , and a (fourth) side plate (not shown), these side plates standing upright so as to extend upward from an outer peripheral edge portion of the bottom plate 51 .
  • These bottom and side plates form a bottom portion (a lower portion) of a (first) casing 55 (in the present embodiment, a compressor casing forming the turbo chiller compressor 3 C).
  • the bottom plate 51 is a plate-shaped member extending in an axial direction and a right-left direction and having a rectangular shape as viewed in the plane.
  • the side plate 52 is a plate-shaped member positioned on a side close to a (second) casing 15 (in the present embodiment, a motor casing forming the electric motor 2 ) attached to one end of the casing 55 and extending in the vertical direction.
  • a (second) casing 15 in the present embodiment, a motor casing forming the electric motor 2
  • the side plate 53 is a plate-shaped member positioned on a side close to a (third) casing 16 (in the present embodiment, a compressor inlet casing forming an inlet of the turbo chiller compressor 3 C) attached to the other end of the casing 55 and extending in the vertical direction.
  • a (third) casing 16 in the present embodiment, a compressor inlet casing forming an inlet of the turbo chiller compressor 3 C
  • the side plate 54 is a plate-shaped member positioned on one end side (the near side on the plane of paper of FIG. 3 ) of the bottom plate 51 , extending in the axial direction and the vertical direction, and having a rectangular shape as viewed in the plane.
  • the not-shown side plate is a plate-shaped member positioned on the other end side (the far side on the plane of paper of FIG. 3 ) of the bottom plate 51 , extending in the axial direction and the vertical direction, and having a rectangular shape as viewed in the plane.
  • a strip-shaped (sheet-shaped) (electric) heater 61 is attached so as to cover outer surfaces of the bottom plate 51 , the side plate 54 , and the not-shown side plate.
  • Strip-shaped (sheet-shaped) metal e.g., SUS430 having a high coefficient of thermal conductivity (having excellent thermal conductivity) is interposed between the heater 61 and each of the outer surfaces of the bottom plate 51 , the side plate 54 , and the not-shown side plate, the metal closely adhering to all of the heater 61 and the outer surfaces of the plates.
  • the heater 61 is replaced or checked only by detachment and attachment of the heater 61 attached to the outer surfaces of the bottom plate 51 , the side plate 54 , and the not-shown side plate.
  • the heater 61 can be replaced or checked without removing oil (not shown) from the oil tank 50 and removing refrigerant from the turbo chiller 1 C.
  • the sheet-shaped metal (not shown) having a high coefficient of thermal conductivity is interposed between the heater 61 and each outer surface so as to closely adhere to all of the heater 61 and the outer surfaces.
  • the coefficient of thermal conductivity from the heater 61 to an outer surface of the oil tank 50 can be increased, and therefore, a low-power heater can be employed.
  • the heater 61 attached to the oil tank 50 can be replaced or checked without removing oil from the oil tank 50 and removing refrigerant from the turbo chiller 1 C.
  • turbo chiller compressor 3 C of the present embodiment since the heater 61 attached to the oil tank 50 can be replaced or checked without removing oil from the oil tank 50 and removing refrigerant from the turbo chiller 1 C, a working time required for replacement or checking of the heater 61 can be significantly reduced, and therefore, the operation rate and reliability of the turbo chiller compressor 3 C can be improved.
  • the working time required for replacement or checking of the heater 61 attached to the oil tank 50 of the turbo chiller compressor 3 C is significantly reduced.
  • the operation rate and reliability of the turbo chiller 1 C can be improved.
  • An oil tank of a turbo chiller compressor of a fourth embodiment of the present invention, a turbo chiller compressor including the oil tank of the turbo chiller compressor of the fourth embodiment of the present invention, and a turbo chiller including the turbo chiller compressor of the fourth embodiment of the present invention will be described below with reference to FIG. 4 .
  • a turbo chiller 1 D of the present embodiment is, for example, placed at a building or a factory in order to generate coolant water for adjusting air.
  • the turbo chiller 1 D includes a turbo chiller compressor (a turbo compressor) 3 D rotatably driven by an electric motor 2 to compress refrigerant vapor into high-pressure vapor, an evaporator (not shown) configured to evaporate chilled water, a condenser (not shown) configured to cool high-pressure vapor with coolant water to condense the high-pressure vapor, and an expander (not shown) configured to expand, by reducing the pressure of condensed refrigerant, the condensed refrigerant to send the expanded refrigerant to the evaporator.
  • the turbo chiller compressor 3 D, the evaporator, the condenser, and the expander are connected together with refrigerant pipes (not shown) through which refrigerant circulates.
  • an oil tank 70 of the turbo chiller compressor 3 D of the present embodiment includes a bottom plate 71 , a (first) side plate 72 , a (second) side plate 73 , a (third) side plate (not shown), and a (fourth) side plate (not shown), these side plates standing upright so as to extend upward from an outer peripheral edge portion of the bottom plate 71 .
  • These bottom and side plates form a bottom portion (a lower portion) of a (first) casing 74 (in the present embodiment, a compressor casing forming the turbo chiller compressor 3 D).
  • the bottom plate 71 is a plate-shaped member extending in an axial direction and a right-left direction and having a rectangular shape as viewed in the plane.
  • the side plate 72 is a plate-shaped member positioned on a side close to a (second) casing 15 (in the present embodiment, a motor casing forming the electric motor 2 ) attached to one end of the casing 74 and extending in the vertical direction.
  • a (second) casing 15 in the present embodiment, a motor casing forming the electric motor 2
  • the side plate 73 is a plate-shaped member positioned on a side close to a (third) casing 16 (in the present embodiment, a compressor inlet casing forming an inlet of the turbo chiller compressor 3 D) attached to the other end of the casing 74 and extending in the vertical direction.
  • a (third) casing 16 in the present embodiment, a compressor inlet casing forming an inlet of the turbo chiller compressor 3 D
  • a hole 81 is formed so as to extend, in the axial direction, from a vertically-extending end surface of the bottom plate 71 positioned on the side close to the casing 15 toward a vertically-extending end surface of the bottom plate 71 positioned on the side close to the casing 16 .
  • the hole 81 is formed with a (first) hole 84 which is positioned on the near side (the side close to the casing 15 ) of the bottom plate 71 and which receives an external thread portion of a screw joint 83 provided at a base end portion of a rod-shaped (electric) heater (a heating means) 82 and a (second) hole 85 which is positioned on the far side (the far side of the hole 84 ) of the bottom plate 71 and into which the heater 82 is inserted.
  • a (first) hole 84 which is positioned on the near side (the side close to the casing 15 ) of the bottom plate 71 and which receives an external thread portion of a screw joint 83 provided at a base end portion of a rod-shaped (electric) heater (a heating means) 82 and a (second) hole 85 which is positioned on the far side (the far side of the hole 84 ) of the bottom plate 71 and into which the heater 82 is inserted.
  • An internal thread portion which comes into engagement with the external thread portion formed at an outer peripheral surface of the screw joint 83 is formed at an inner peripheral surface of the hole 84 .
  • the heater 82 is inserted into the hole 81 , and a space between the hole 81 and the heater 82 is filled with heat transfer fluid 88 (e.g., a heat-resistant release silicon material, chemically-synthesized oil, and a boron nitride aqueous solution) having a high coefficient of thermal conductivity (having excellent thermal conductivity).
  • heat transfer fluid 88 e.g., a heat-resistant release silicon material, chemically-synthesized oil, and a boron nitride aqueous solution
  • a plurality of heat transfer fins 86 (in the present embodiment, eight heat transfer fins 86 ) having a corrugated shape as viewed in the cross section are formed at an upper surface (an internal surface) of the bottom plate 71 .
  • the heat transfer fins 86 are formed so as to protrude upward from the upper surface of the bottom plate 71 , and continuously extend, in the vertical direction and the right-left direction, from an inner surface (an internal surface) of the (third) side plate (not shown) to an inner surface (an internal surface) of the (fourth) side plate (not shown).
  • a reference numeral “ 87 ” in FIG. 4 denotes oil (lubrication oil).
  • the plurality of heat transfer fins 86 are formed so as to protrude upward from the upper surface of the bottom plate 71 , and therefore, the contact area between the oil 87 and the bottom plate 71 heated by the heater 82 can be increased.
  • the oil 87 can be more efficiently heated, and as a result, a lower-power heater can be employed.
  • the space between the protective tube 22 and the heater 26 is filled with the heat transfer fluid 88 having a high coefficient of thermal conductivity.
  • this heat transfer fluid 88 is not essential.
  • the space between the hole 41 and the heater 42 is filled with the heat transfer fluid 88 having a high coefficient of thermal conductivity.
  • this heat transfer fluid 88 is not essential.
  • the strip-shaped metal having a high coefficient of thermal conductivity is interposed between the heater 61 and each of the outer surfaces of the bottom plate 51 , the side plate 54 , and the not-shown side plate so as to closely adhere to all of the heater 61 and the outer surfaces.
  • this metal is not essential.
  • the configuration in which the heater 61 is attached so as to cover the outer surfaces of the bottom plate 51 , the side plate 54 , and the not-shown side plate has been described as one specific example.
  • the present invention is not limited to this example, and the heater can be attached so as to only cover the outer surface of the bottom plate 51 .
  • thermometer configured to measure an oil temperature
  • second thermometer configured to measure an oil tank temperature
  • a heat-retaining material is more preferably provided so as to cover the entirety of the outer portion of the oil tank in above-described first, second, and fourth embodiments and to cover the entirety of the outer portions of the oil tank and the heater in the third embodiment.
  • the heaters 42 , 82 are more preferably formed of four heaters each having a capacity of 500 W (having a total capacity of 2000 W).
  • all of the four heaters can be used to heat the oil tanks 30 , 70 .
  • the temperature of the oil tanks 30 , 70 is higher than 30° C. and lower than 50° C.
  • three of the four heaters can be used to heat the oil tanks 30 , 70 .
  • the temperature of the oil tanks 30 , 70 is equal to or higher than 50° C.
  • two of the four heaters can be used to heat the oil tanks 30 , 70 .
  • the amount of heating of the oil tanks 30 , 70 by the heaters 42 , 82 can be reduced, and as a result, the amount of heat dissipation to the surrounding atmosphere can be reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
US14/768,326 2013-03-06 2014-02-13 Oil tank of turbo chiller compressor and turbo chiller compressor Active 2034-05-06 US9856885B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2013-044010 2013-03-06
JP2013044010A JP6223696B2 (ja) 2013-03-06 2013-03-06 ターボ冷凍機用圧縮機のオイルタンクおよびターボ冷凍機用圧縮機
PCT/JP2014/053255 WO2014136540A1 (ja) 2013-03-06 2014-02-13 ターボ冷凍機用圧縮機のオイルタンクおよびターボ冷凍機用圧縮機

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US20160010654A1 US20160010654A1 (en) 2016-01-14
US9856885B2 true US9856885B2 (en) 2018-01-02

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JP (1) JP6223696B2 (OSRAM)
CN (2) CN110307176A (OSRAM)
DE (1) DE112014001139T5 (OSRAM)
MY (1) MY183372A (OSRAM)
SG (1) SG11201506716YA (OSRAM)
WO (1) WO2014136540A1 (OSRAM)

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Publication number Priority date Publication date Assignee Title
JP2018169059A (ja) * 2017-03-29 2018-11-01 三菱重工サーマルシステムズ株式会社 冷凍機
CN107218711B (zh) * 2017-07-31 2019-11-08 青岛海信日立空调系统有限公司 一种空调器及其控制方法
DE102020117899B4 (de) 2020-07-07 2022-11-17 SPH Sustainable Process Heat GmbH Hochtemperaturwärmepumpe
CN114645876A (zh) * 2022-03-24 2022-06-21 诺文科智能通风研究院(西安)有限公司 具有限制性消音结构的低噪音通风机及其方法

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SG11201506716YA (en) 2015-09-29
DE112014001139T5 (de) 2015-11-19
WO2014136540A1 (ja) 2014-09-12
JP6223696B2 (ja) 2017-11-01
US20160010654A1 (en) 2016-01-14
JP2014173435A (ja) 2014-09-22
CN110307176A (zh) 2019-10-08
MY183372A (en) 2021-02-18
CN105026770A (zh) 2015-11-04

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